Refrigerator

ABSTRACT

A refrigerator may include a compressor to compress a refrigerant, a condenser to condense the refrigerant having passed through compressor, a capillary tube to lower a temperature and a pressure of the refrigerant having passed though the condenser, an evaporator to evaporate the refrigerant having passed through the capillary tube, and a heat exchanger coupled to a refrigerant pipe connected to the compressor to cool the refrigerant in the refrigerant pipe. With components so arranged, operational efficiency of the refrigerator may be enhanced, and energy may be saved.

CROSS-REFERENCE TO RELATED APPLICATION(S)

This application claims priority under 35 U.S.C. §119 to Korean Application Nos. 10-2012-0120276 filed in Korea on Oct. 29, 2012 and 10-2012-0128559 filed in Korea on Nov. 14, 2012, whose entire disclosures are hereby incorporated by reference.

BACKGROUND

1. Field

This relates to a refrigerator, and more particularly, to a refrigerator which has an enhanced operational efficiency.

2. Background

A refrigerator freeze food or keep the food in a cooled state, may include a case forming an accommodation space divided into a freezer compartment and a refrigeration compartment, and devices such as a compressor, a condenser, an evaporator, and capillary tubes forming a refrigeration cycle. A door may be coupled to the case to open and close the freezer compartment and refrigeration compartment. The compressor may compress a gaseous refrigerant in a low temperature and low pressure state to a high temperature and high pressure state. While passing through the condenser, the compressed gaseous refrigerant may be cooled and condensed to a high-pressure liquid refrigerant. The temperature and pressure of the high-pressure liquid refrigerant may be lowered as the refrigerant passes through the capillary tube. The refrigerant may then change to the gaseous state at low temperature and low pressure in the evaporator, absorbing heat.

BRIEF DESCRIPTION OF THE DRAWINGS

The embodiments will be described in detail with reference to the following drawings in which like reference numerals refer to like elements wherein:

FIG. 1 is a schematic view of refrigeration cycle of a refrigerator according to a first embodiment as broadly described herein;

FIG. 2 illustrates a machine room in which components of the refrigeration cycle shown in FIG. 1 are received;

FIG. 3 is a perspective view of a portion of the machine room shown in FIG. 2;

FIG. 4 is a side view of a heat exchange device;

FIG. 5 is a schematic view of a refrigeration cycle according to another embodiment as broadly described herein;

FIG. 6 illustrates a machine room in which components of the refrigeration cycle shown in FIG. 5 are received;

FIG. 7 is a perspective view of a refrigerator according to a an embodiment as broadly described herein;

FIG. 8 is a schematic view of a refrigeration cycle of the refrigerator shown in FIG. 7;

FIG. 9 illustrates a machine room of the refrigerator shown in FIGS. 7 and 8;

FIG. 10 is a perspective view of a portion of the machine room shown in FIG. 9;

FIG. 11 is a view of a heat exchange device;

FIG. 12 illustrates a machine room in accordance with another embodiment as broadly described herein;

FIG. 13 is a perspective view of a portion of the machine room shown in FIG. 12;

FIG. 14 is a schematic view of a refrigeration cycle according to another embodiment as broadly described herein;

FIG. 15 is a schematic view of a refrigeration cycle according to another embodiment as broadly described herein; and

FIG. 16 is a schematic view of a refrigeration cycle according to another embodiment as broadly described herein.

DETAILED DESCRIPTION

Reference will now be made in detail to the various embodiments, examples of which are illustrated in the accompanying drawings. It may be appreciated that for simplicity and clarity of illustration, the dimensions and shapes of some of the elements may be exaggerated relative to other elements. In addition, terms specifically defined in consideration of the configuration and operation embodiments as broadly described herein may be differently defined according to intention of an operator or practices. These terms may be defined based on the entire context of this disclosure.

A refrigerator according to a first embodiment as broadly described herein may include a compression unit 110, or compressor 110, to compress a refrigerant, a condensation unit 120, or condenser 120, to condense the refrigerant having passed through the compression unit 110, a capillary tube 130 to decrease the temperature and pressure of the refrigerant having passed through the condensation unit 120, and an evaporation unit 140, or evaporator 140, to evaporate the refrigerant having passed through the capillary tube 130. The refrigeration cycle is implemented as the refrigerant sequentially passes through the compression unit 110, the condensation unit 120, and the capillary tube 130, supplies coldness to the external air in the evaporation unit 140, and then undergoes compression in the compression unit 110.

The refrigerator further includes a first refrigerant pipe 150 to connect the compression unit 110 to the condensation unit 120 and a second refrigerant pipe 160 to connect the evaporation unit 140 to the compression unit 110. The refrigerant is guided from the compression unit 110 to the condensation unit 120 through the first refrigerant pipe 150, and guided from the evaporation unit 140 to the compression unit 110 through the second refrigerant pipe 160.

The refrigerator further includes a heat exchange unit 200, or heat exchanger 200, provided with the first refrigerant pipe 150 and the second refrigerant pipe 160 contacting each other to exchange heat with each other. The heat exchange unit 200 is configured to have the first refrigerant pipe 150 and the second refrigerant pipe 160 contacting each other such that heat exchange occurs between the refrigerant passing through the first refrigerant pipe 150 and the refrigerant passing through the second refrigerant pipe 160.

That is, heat exchange may occur while the refrigerant moves along the first refrigerant pipe 150 and the second refrigerant pipe 160, and moves from position c to position d and from position a to position b in the heat exchange unit 200. Since the refrigerant passing through the heat exchange unit 200 is individually and independently guided in the first refrigerant pipe 150 and the second refrigerant pipe 160, the refrigerants in the first refrigerant pipe 150 and the second refrigerant pipe 160 may move without being mixed with each other in the heat exchange unit 200. That is, the refrigerants passing through the first refrigerant pipe 150 and the second refrigerant pipe 160 may be independent from each other, and may exchange heat with each other through the heat exchange unit 200 without affecting movement of the other.

A gaseous refrigerant at a relatively high temperature may be present in the first refrigerant pipe 150, while a gaseous refrigerant at a relatively low temperature may be present in the second refrigerant pipe 160.

Typically, the refrigerant guided from the compression unit 110 to the condensation unit 120 through the first refrigerant pipe 150 remains in a gaseous state at about 50 degrees Celsius, which is the highest temperature in the path of the refrigeration cycle in which the refrigerant circulates. This is because the temperature of the refrigerant increases as the refrigerant is compressed in the compression unit 110, and the first refrigerant pipe 150 provides the flow path for the refrigerant exiting the compression unit 110. The overall temperature of the refrigerant may decrease while the refrigerant flows through the first refrigerant pipe 150.

On the other hand, the refrigerant guided from the evaporation unit 140 to the compression unit 110 through the second refrigerant pipe 160 is in a gaseous state at about −10 degrees Celsius. The refrigerant in the second refrigerant pipe 160 is introduced into the compression unit 110 and compressed after supplying coldness to the outer space through the evaporation unit 140. Accordingly, in view of the overall refrigeration cycle, the remaining coldness held by the refrigerant having passed through the second refrigerant pipe 160 is substantially wasted energy that is not supplied to the outer space. That is, the refrigerant guided to the compression unit 110 through the second refrigerant pipe 160 fails to supply coldness to the outer space through the second refrigerant pipe 160, and accordingly the temperature thereof increases. The refrigerant would typically waste coldness while moving through the second refrigerant pipe 160.

According to this embodiment, the coldness of the refrigerant otherwise wasted through the second refrigerant pipe 160 is used to decrease the temperature of the refrigerant passing through the first refrigerant pipe 150, which has the highest temperature in the refrigeration cycle, and thus the operational efficiency of the refrigeration cycle may be enhanced. That is, the temperature of the refrigerant passing through the first refrigerant pipe 150 decreases, and thereby the temperature of the refrigerant guided to the evaporation unit 140 is lowered. As a result, the portion of coldness supplied to the outer space through the evaporation unit 140 may increase.

FIGS. 2 and 3 illustrate the machine room in which various components of the refrigeration cycle may be housed. In FIGS. 2 and 3, pipes through which the refrigerant moves and other constituents unnecessary for the description are omitted for simple and clear illustration.

The refrigerator may include a machine room 2 in which the compression unit 110 and the condensation unit 120 are installed. The machine room 2 may be arranged at the lower portion of the refrigerator body. Alternatively, the machine room 2 may be arranged at the upper portion of the refrigerator, unlike the configuration shown in FIGS. 2 and 3. The machine room 2 is a space where various constituents of the refrigerator are installed. Unlike the refrigeration compartment or the freezer compartment, the machine room 2 allows introduction of external air and discharge of internal air.

In the case that the machine room 2 is arranged at the lower portion of the refrigerator, storage compartments including the refrigeration compartment and the freezer compartment may be provided above the machine room 2. In addition, the evaporation unit 140 to supply coldness to the refrigeration compartment and the freezer compartment may be installed to adjoin the refrigeration compartment and the freezer compartment, rather than being installed in the machine room 2, and the pipe to guide the refrigerant to the evaporation unit 140 may extend out of the machine room 2 to the refrigeration compartment and the freezer compartment. Herein, part of the pipe may be installed between the inner case and outer case of the refrigerator body. An insulating material may be introduced into the space between the inner case and the outer case and foamed to insulate the pipe. Thereby, the pipe installed between the inner case and the outer case is prevented from exchanging heat with the external air.

Plural pipes to guide flow of the refrigerant may be installed in the machine room 2, and a fan 80 to cool the compression unit 110 and the condensation unit 120 may be provided in the machine room 2, such that the refrigerant circulates in the refrigeration cycle.

The fan 80 may be disposed between the compression unit 110 and the condensation unit 120. Thereby, the compression unit 110 and the condensation unit 120 may be cooled by one fan 80. That is, when the fan 80 is driven, one of the compression unit 110 or the condensation unit 120 may be cooled by the external air drawn into the machine room 2 by the fan 80, before it is introduced into the fan 80, and the other of the compression unit 110 or the condensation unit 120 may be cooled by the air discharged from the fan 80. At this time, the fan 80 may operate only when the compression unit 110 is driven. Whether or not the compression unit 110 is driven may be determined by a separate temperature sensor.

The refrigerant may be guided from the compression unit 110 installed in the machine room 2 to the heat exchange unit 200 through the first refrigerant pipe 150. When passing through the heat exchange unit 200, the refrigerant is guided from position c to position d, and is then moved to the condensation unit 120.

After passing through the evaporation unit 140, the refrigerant is guided to the compression unit 110 through the second refrigerant pipe 160. When passing through the heat exchange unit 200, the refrigerant is guided from position a to position b, and is then moved to the compression unit 110.

The heat exchange unit 200 is arranged in the machine room 2 where the compression unit 110 is installed. The heat exchange unit 200 may be installed to be exposed to the inner space of the machine room 2 to contact the air received in the machine room 2. At typical room temperature, the machine room 2 usually remains at about 32 degrees Celsius. Since the heat exchange unit 200 is exposed to the inner space of the machine room 2, the relatively hot refrigerant passing through the first refrigerant pipe 150, i.e., the refrigerant at about 50 degrees Celsius may be cooled by the air in the machine room 2 through the heat exchange process.

Meanwhile, a part of the second refrigerant pipe 160 may be installed outside the machine room 2. That is, the second refrigerant pipe 160 connects the evaporation unit 140, which may not be installed in the machine room 2 but instead adjacent to the refrigeration compartment or the freezer compartment, to the compression unit 110 to allow movement of the refrigerant. Accordingly, a part of the second refrigerant pipe 160 is installed in the machine room 2 and a part extends out of the machine room 2.

As shown in FIG. 4, the heat exchange unit 200 includes an outer-side part 210, or outer portion 210, connected to the first refrigerant pipe 150, and an inner-side part 220, or inner portion 220, connected to the second refrigerant pipe 160. The outer-side part 210 may surround the inner-side part 220. Since the outer-side part 210 is connected to the first refrigerant pipe 150, through which the relatively hot refrigerant passes, the outer-side part 210 remains at a relatively high temperature. On the other hand, the inner-side part 220 is connected to the second refrigerant pipe 160, through which the relatively cold refrigerant passes, and thus the inner-side part 220 remains at a relatively low temperature.

Herein, the outer-side part 210 may have substantially the same cross sectional area as that of the first refrigerant pipe 150 so as not to influence movement of the refrigerant. In the case that the cross sectional area varies when the refrigerant guided through the first refrigerant pipe 150 enters the outer-side part 210, the pressure of the refrigerant could change, and accordingly movement of the refrigerant could be affected.

Similarly, the inner-side part 220 may have substantially the same cross sectional area as that of the second refrigerant pipe 160 so as not to influence movement of the refrigerant. In the case that the area of cross section varies when the refrigerant guided through the second refrigerant pipe 160 enters the inner-side part 220, the pressure of the refrigerant could change, and accordingly movement of the refrigerant could be affected.

Since the heat exchange unit 200 is installed in the machine room 2 and contacts the air, the outer-side part 210 may exchange heat with the inner-side part 220 positioned therein, while also exchanging heat with the air in the machine room 2. Accordingly, the temperature of the refrigerant passing through the first refrigerant pipe 150 may be effectively lowered. That is, the outer-side part 210 simultaneously exchanges heat with the inner-side part 220 and the air inside machine room 2.

In addition, the inner-side part 220, which remains at a relatively low temperature, does not undergo heat exchange with the air in the machine room 2. Accordingly, a larger portion of coldness of the inner-side part 220 may be transferred to the outer-side part 210.

In the case that the outer-side part 210 remains at a relatively low temperature, coldness of the outer-side part 210 may be transferred to the air in the machine room 2. However, since in embodiments as broadly described herein, the temperature of the refrigerant passing through the first refrigerant pipe 150 is lowered, coldness of the refrigerant passing through the second refrigerant pipe 160 may be transferred to the first refrigerant pipe 150 as much as possible without being wasted to the surroundings. Accordingly, the second refrigerant pipe 160 is not exposed to the air inside the machine room 2.

Since the fan 80 illustrated in FIGS. 2 and 3 causes forced convection heat transfer between the outer-side part 210 and the air in the machine room 2, the efficiency of cooling the refrigerant in the outer-side part 210 may be enhanced. Heat exchange occurs between the outer-side part 210 and the inner-side part 220 by conduction, while heat exchange occurs between the outer-side part 210 and the air in the machine room 2 by convection.

The flow direction of the refrigerant in the outer-side part 210 may be opposite to the flow direction in the inner-side part 220. Since the refrigerant flows in different directions in the outer-side part 210 and the inner-side part 220, better heat exchange may occur between the outer-side part 210 and the inner-side part 220.

Particularly, the outer-side part 210 and the inner-side part 220 may be concentrically arranged. That is, the inner-side part 220 may be formed in the shape of a hollow cylinder, and the outer-side part 210 may be formed in the shape of a hollow cylinder having a larger diameter than the inner-side part 220 and having the inner-side part 220 positioned at the center thereof. Alternatively, the outer-side part 210 and the inner-side part 220 may have a different configuration such that the area of contact therebetween is increased with the area of cross section kept constant.

The second refrigerant pipe 160 may be perpendicularly connected to the outer-side part 210. That is, as shown in FIG. 4, the flow path of the refrigerant moving along the outer-side part 210 may be arranged perpendicular to the flow path of the refrigerant as it is introduced into or discharged from the outer-side part 210 from/to the first refrigerant pipe 150. That is, since the flow path of the refrigerant introduced into the outer-side part 210 from the first refrigerant pipe 150 is perpendicular with respect to the outer-side part 210, sufficient heat exchange may occur between the refrigerant and the surface forming the external shape of the outer-side part 210 due to various types of flows.

In the heat exchange unit 200, the refrigerant moving along the first refrigerant pipe 150 and the refrigerant moving along the second refrigerant pipe 160 make contact or surface contact with each other at plural points. Accordingly, the efficiency of heat exchange between the refrigerant moving along the first refrigerant pipe 150 and the refrigerant moving along the second refrigerant pipe 160 may be enhanced.

In addition, since the heat exchange unit 200 is formed as a single component, separation of the first refrigerant pipe 150 and the second refrigerant pipe 160 from each other due to vibration possibly caused by movement of the refrigerant may be prevented, compared to the case in which the first refrigerant pipe 150 and the second refrigerant pipe 160 are attached to each other through welding. Moreover, the risk of occurrence of noise due to fine vibration caused by separation of the first refrigerant pipe 150 and the second refrigerant pipe 160 from each other is also eliminated.

Hereinafter, operation of the heat exchange unit 200 will be described based on the principle of movement of the refrigerant according to one embodiment of the present invention.

First, the hot refrigerant compressed by the compression unit 110 is guided to the first refrigerant pipe 150. Then, the refrigerant flows along the first refrigerant pipe 150 and passes through the outer-side part 210 of the heat exchange unit 200. At this time, the refrigerant may be guided from position c to position d. Accordingly, the temperature of the outer-side part 210 may be increased due to the temperature of the refrigerant, and may be partially lowered due to the temperature of the air in the machine room 2.

At this time, the fan 80 is driven to cause forced convection between the inner space of the machine room 2 and the outer-side part 210. Thereby, the outer-side part 210 may be cooled by convection.

After being discharged from the outer-side part 210, the refrigerant may be guided to the condensation unit 120 through the first refrigerant pipe 150 and condensed in the condensation unit 120. Then, the refrigerant may supply coldness thereof to the refrigeration compartment or the freezer compartment while passing through the capillary tube unit 130 and the evaporation unit 140. The refrigerant may supply coldness to the external area by being cooled to about −20 degrees Celsius in the evaporation unit 140.

After being discharged from the evaporation unit 140, the refrigerant is guided to the inner-side part 220 of the heat exchange unit 200 through the second refrigerant pipe 160. At this time, the refrigerant may be guided from position a to position b.

Even after the refrigerant supplies coldness to the outside of the evaporation unit 140 by passing through the evaporation unit 140, the temperature of the refrigerant is relatively low. Therefore, while passing through the inner-side part 220, the refrigerant may cool the refrigerant passing through the outer-side part 210.

Particularly, since the inner-side part 220 and the outer-side part 210 make surface contact with each other at plural points, the refrigerant passing through the inner-side part 220 may efficiently cool the refrigerant passing through the outer-side part 210. For example, without the heat exchange unit 200, the coldness held by the refrigerant guided to the second refrigerant pipe 160 may be wasted without being used. In this embodiment, the coldness held by the refrigerant having passed through the evaporation unit 140 is used to cool the refrigerant circulating in the refrigeration cycle. Therefore, the overall efficiency of the refrigeration cycle may be improved.

Furthermore, since flows of the refrigerant in the inner-side part 220 and the outer-side part 210 are in opposite directions, the heat exchange efficiency may be improved due to the different way of heat transfer to the flows of the refrigerant.

In experimentation with the heat exchange unit 200, or heat exchanger 200, as embodied and broadly described herein, it has been found that the power consumption may be improved by about 2.5%. Specifically, in a case in which this type of heat exchange unit was not adopted, 60.1 watts (W) was needed to operate the refrigeration cycle. In contrast, by employing the above described heat exchange unit 200, it was possible to operate the refrigeration cycle with 58.7 W.

FIG. 5 illustrates a refrigeration cycle according to another embodiment as broadly described herein. In this embodiment, two compression units, or compressors, are provided, in contrast with the previous embodiment illustrated in FIG. 1. The components other than the two compression units are substantially the same as those of the previous embodiment, and thus a description thereof will be omitted.

The compression units may include a first compression unit 112, or first compressor 112, to primarily compress the refrigerant guided thereinto from the evaporation unit 140, or evaporator 140, and a second compression unit 114, or second compressor 114, to secondarily compress the refrigerant compressed by the first compression unit 112 and guide the same to the condensation unit 120, or condenser 120.

After being compressed by the first compression unit 112, the refrigerant is additionally compressed while passing through the second compression unit 114. The compressed gaseous refrigerant may be supplied to the condensation unit 120. While the refrigerant passes through the second compression unit 114, the pressure thereof is increased. Accordingly, the temperature of the refrigerant guided from the second compression unit 114 to the condensation unit 120 may be higher than in any other constituents of the refrigeration cycle.

FIG. 6 illustrates a machine room in which various components of the refrigeration cycle are housed. In FIG. 6, pipes through which the refrigerant moves and other constituents unnecessary for the description are omitted for simple and clear illustration. In addition, to simplify the illustration, components associated with the pipe through which the refrigerant discharged from the first compression unit 112 is guided to the second compression unit 114 are omitted in FIG. 6. Compared to the previous embodiment in FIG. 2, the condensation unit 120 is disposed at a position other than the machine room 2.

After being compressed in the first compression unit 112 and the second compression unit 114, the refrigerant is guided to the heat exchange unit 200 through the first refrigerant pipe 150. Herein, when the refrigerant passes through the heat exchange unit 200, it may be guided from position c to position d. After passing through the heat exchange unit 200, the refrigerant is guided to the condensation unit 120 through the first refrigerant pipe 150.

On the other hand, the refrigerant having passed through the evaporation unit 140 is guided to the heat exchange unit 200 through the second refrigerant pipe 160. When passing through the heat exchange unit 200, the refrigerant may be guided from position a to position b. After passing through the heat exchange unit 200, the refrigerant may be guided to the first compression unit 112 through the second refrigerant pipe 160.

That is, in the heat exchange unit 200, one stream of the refrigerant is guided from position a to position b, and the other stream of the refrigerant is guided from position c to position d.

The shape and operation of the heat exchange unit 200 are the same as those described above with reference to FIG. 4. In the heat exchange unit 200, heat exchange may occur between the outer-side part 210 and the air in the machine room by convection, while heat exchange may occur between the outer-side part 210 and the inner-side part 220 by conduction. The heat exchange unit 200 according to this embodiment operates in the same manner as in the previous embodiment, and therefore a detailed description thereof will be omitted.

Next, a refrigerator according to another embodiment will be described with reference to FIGS. 7 to 15.

As shown in FIG. 7, the refrigerator according to this embodiment includes a body 1, a storage compartment 3 provided in the body 1, and a door 5 to open and close the storage compartment 3. The door 5 is pivotably arranged at the body 1. An ice making compartment 23 to make and store ice and a dispenser 40 to dispense water are installed at the door 5. An ice maker 26 to make ice and an ice storage case 29 to store ice made by and removed from the ice maker 26 are installed in the ice making compartment 23. Arranged at the lower portion of the ice making compartment 23 is a water tank 13 to store water to be supplied to the dispenser 40 in a cooled state. A flow path control valve 33 to selectively or simultaneously guide water to the dispenser 40 and the ice maker 26 is arranged at one side of the water tank 13.

The flow path control valve 33 may be a three-way valve having one discharge portion connected to the water tank 13 and the other discharge portion connected to the ice maker 26. Herein, the flow path control valve 33 may selectively or simultaneously supply water to the water tank 13 and the ice maker 26. That is, the flow path control valve 33 may configured to supply water to only one of the water tank 13 or the ice maker 26, or to both the water tank 13 and the ice maker 26.

In addition, a flow sensor 16 to calculate the flow rate of water is provided at the inlet side of the flow path control valve 33. Herein, the flow sensor 16 is a device that measures the flow rate of water supplied to the ice maker 26 or the dispenser 40 when the flow path control valve 33 guides water to the ice maker 26 or the dispenser 40. The flow sensor 16 is mounted to a second water hose 54, which is connected to an external water source 50. A water supply valve 12 and a filter 14 to filter water are arranged between the flow sensor 16 and the external water source 50.

The water supply valve 12 functions to open and close the flow path along which water flows from the external water source 50 into the refrigerator. That is, when the water supply valve 12 opens the flow path, water may flow from the external water source 50 into the refrigerator. When the water supply valve 12 closes the flow path, water is not allowed to flow from the external water source 50 into the refrigerator.

An outlet-side water supply valve may be provided to the ice maker 26 or the dispenser 40 to open and close flow path along which water flows. Herein, the outlet-side water supply valve includes a second water supply valve 17 and a third water supply valve 18.

Herein, the second water hose 54 is disposed along one side of the body 1 and arranged to extend through a hinge 60 connecting the door 5 to the body 1 and be connected to the flow sensor 16 and the flow path control valve 33 along one side of the door 5.

A first connection hose 19 connected to the one discharge portion of the flow path control valve 33 is connected to the water tank 33 and the dispenser 40. Herein, the third water supply valve 18 to open and close the flow path for water moving to the dispenser 40 is arranged in the first connection hose 19. When the third water supply valve 18 opens the flow path, water may be supplied to the dispenser 40 through the first connection hose 19.

A second connection hose 56 connected to the other discharge portion of the flow path control valve 33 is disposed to extend upward along one side of the door 5 and to transport water to an ice-making tray 27. Herein, the second water supply valve 17 to open and close the flow path along which water moves to the ice maker 26 is arranged in the second connection hose 56. When the second water supply valve 17 opens the flow path, water may be supplied to the ice maker 26 through the second connection hose 56.

Herein, the inner space of the ice making compartment 23 is closed by an ice making compartment door pivotably provided to one sidewall of the ice making compartment 23. Thereby, the inner space of the ice making compartment 23 is differentiated from the interior of the storage compartment 3.

Meanwhile, the external water source 50 is connected to the water supply valve 12 via a connection pipe 51. The connection pipe 51 is always filled with water according to water pressure supplied by the external water source 50. The water contained in the connection pipe 51 moves through the water supply valve 12 when the water supply valve 12 opens the flow path. On the other hand, when the water supply valve 12 closes the flow path, the water remains stationary in the connection pipe 51.

Meanwhile, the water supply valve 12 and the filter 14 are sequentially connected by the first water hose 52 and the second water hose 54. A heat exchange unit 300, or heat exchanger 300, is arranged between the first water hose 52 and the second water hose 54, and accordingly water having passed through the first water hose 52 may move to the second water hose 54. The heat exchange unit 300 may be capable of cooling the refrigerant circulating in the refrigeration cycle.

The water supply valve 12 is connected to the heat exchange unit 300 via the first water hose 52, and the heat exchange unit 300 is connected to the filter 14 via the second water hose 54. Accordingly, the water supplied from the external water source 50 passes through the first water hose 52 and then through the heat exchange unit 300. Then the water is guided to the filter 14 via the second water hose 54.

At this time, the temperature of the water supplied from the external water source 50 may be equal to or lower than the room temperature. Typically, water supplied from an external source through water pipes is moved to homes or offices via the underground. Accordingly, the temperature of the supplied water is usually lower than the room temperature. Particularly, in the case that the external water source 50 is underground water, the temperature of the supplied water is lower than the room temperature.

FIG. 8 illustrates a refrigeration cycle of the refrigerator shown in FIG. 7, according to an embodiment. The refrigerator according to this embodiment includes a compression unit 110, or compressor 110, to compress a refrigerant, a condensation unit 120, or condenser 120, to condense the refrigerant having passed through the compression unit 110, a capillary tube 130 to decrease the temperature and pressure of the refrigerant having passed through the condensation unit 120, and an evaporation unit 140, or evaporator 140, to evaporate the refrigerant having passed through the capillary tube 130. The refrigeration cycle is implemented as the refrigerant sequentially passes through the compression unit 110, the condensation unit 120, and the capillary tube unit 130, supplies coldness to the external air in the evaporation unit 140, and then undergoes compression in the compression unit 110.

In the compression unit 110, the heat exchange unit 300, or heat exchanger 300, is installed at the first refrigerant pipe 150 connected to the condensation unit 120. The first refrigerant pipe 150 extending through the heat exchange unit 300 is arranged to perform heat exchange with water in the heat exchange unit 300, and is provided with an independent flow path along which the refrigerant flows without being mixed with water in the heat exchange unit 300.

The heat exchange unit 300 is connected to the first water hose 52 and the second water hose 54 to allow water to pass through the heat exchange unit 300. That is, heat exchange may occur between water and the refrigerant in the heat exchange unit 300 by conduction. Thereby, the water whose temperature is relatively low may lower the temperature of the refrigerant. That is, in the heat exchange unit 300, heat exchange may occur between the water guided by the first water hose 52 and the second water hose 54 and the refrigerant flowing along the first refrigerant pipe 150.

The temperature of the refrigerant circulating in the refrigeration cycle usually increases to the highest temperature as the refrigerant from the compression unit 110 flows through the condensation unit 120. This is because the compression unit 110 compresses the refrigerant, thereby causing the temperature of the compressed refrigerant to increase.

Meanwhile, the water supplied from the external water source 50 is guided to the heat exchange unit 300 only through the water supply valve 12, and thus the temperature thereof remains substantially constant. Accordingly, as heat exchange occurs between the water, which is at a relatively low temperature, and the refrigerant passing through the first refrigerant pipe 150, the temperature of the refrigerant may be lowered.

Further, the amount of the refrigerant in the refrigeration cycle in the refrigerator is not so large. Accordingly, even if heat exchange occurs between the water and the refrigerant in the heat exchange unit 300, the temperature of the water, the amount of which is relatively large, does not greatly increase. Therefore, the temperature of the water is not increased that much when it is supplied to the user. As a result, the efficiency of the refrigeration cycle may be enhanced by lowering the temperature of the refrigerant, without causing great inconvenience to the user.

Unlike the embodiment illustrated in FIG. 8, the heat exchange unit 300 may be installed at a third refrigerant pipe 170 connecting the condensation unit 120 to the capillary tube 130. A related embodiment will be described later with reference to FIG. 14.

As shown in FIGS. 9 and 10, the refrigerator shown in FIGS. 7 and 8 may include a machine room 2 in which the compression unit 110 and the condensation unit 120 are installed. The machine room 2 may be arranged at the lower portion of the refrigerator body 1. Alternatively, the machine room 2 may be arranged at the upper portion of the refrigerator, unlike the configuration shown in FIGS. 9 and 10.

Plural pipes to guide flow of the refrigerant may be installed in the machine room 2, and a fan 80 to cool the compression unit 110 and the condensation unit 120 may be provided in the machine room 2, such that the refrigerant circulates in the refrigeration cycle.

The heat exchange unit 300 is arranged in the machine room 2 where the compression unit 110 is installed. The heat exchange unit 300 may be installed to be exposed to the inner space of the machine room 2 to contact the air received in the machine room 2. At room temperature, the machine room 2 usually remains at about 32 degrees Celsius. Since the heat exchange unit 300 is exposed to the inner space of the machine room 2, the relatively hot refrigerant passing through the first refrigerant pipe 150, i.e., the refrigerant at about 50 degrees Celsius may be cooled by the air in the machine room through the heat exchange process.

Meanwhile, the first refrigerant pipe 150 is cooled in the heat exchange unit 300 not by air but by water. Accordingly, the temperature of the refrigerant may be greatly decreased while the refrigerant passes through the first refrigerant pipe 150. This is because the efficiency of cooling by water is generally greater than by air.

A connection pipe 51 to guide water from the external water source 50 to the water supply valve 12 is installed at one side of the water supply valve 12. In addition, a first water hose 52 to guide water to the heat exchange unit 300 is installed at the water supply valve 12. According to opening and closing of the flow path by the water supply valve 12, water in the connection pipe 51 may be guided to the first water hose 52 and moved to the heat exchange unit 300.

As shown in FIG. 11, the heat exchange unit 300 includes an outer-side part 310, or outer portion 310, connected to the first refrigerant pipe 150, and an inner-side part 320, or inner portion 320, connected to the first water hose 52 and the second water hose 54. The outer-side part 310 may be arranged to surround the inner-side part 320. Since the outer-side part 310 is connected to the first refrigerant pipe 150, through which the relatively hot refrigerant passes, the outer-side part 310 remains at a relatively high temperature. On the other hand, the inner-side part 320 is connected to the first water hose 52 and the second water hose 54, through which the relatively cold water passes, and thus the inner-side part 320 remains at a relatively low temperature.

Herein, the outer-side part 310 may have substantially the same cross sectional area as that of the first refrigerant pipe 150 so as not to influence movement of the refrigerant. In a case in which the cross sectional area varies when the refrigerant guided through the first refrigerant pipe 150 enters the outer-side part 310, the pressure of the refrigerant may change, and accordingly movement of the refrigerant may be affected.

Similarly, the inner-side part 320 may have substantially the same cross sectional area as that of the first water hose 52 and the second water hose 54 so as not to influence movement of the refrigerant. Unlike the outer-side part 310, however, the cross sectional area of the inner-side part 320 may be different from that the first water hose 52 and the second water hose 54, because a change in flow rate of the water flowing through the first water hose 52 and the second water hose 54 does not produce a large load to the ice maker 26 or the dispenser 40.

Since the heat exchange unit 300 is installed in the machine room 2 to contact the air contained therein, the outer-side part 310 may exchange heat with the inner-side part 320 positioned therein, while exchanging heat with the air in the machine room 2. Accordingly, the temperature of the refrigerant passing through the first refrigerant pipe 150 may be effectively lowered. That is, the outer-side part 310 simultaneously exchanges heat with the inner-side part 320 and the air inside machine room 2. In addition, the inner-side part 320, which remains at a relatively low temperature, does not undergo heat exchange with the air in the machine room 2. Accordingly, a larger portion of coldness of the water in the inner-side part 320 may be transferred to the outer-side part 310

In a case in which the outer-side part 310 remains at a relatively low temperature, coldness of the outer-side part 310 may be used to cool the air in the machine room 2. However, in order to lower the temperature of the refrigerant passing through the first refrigerant pipe 150, coldness of the water passing through the first water hose 52 and the second water hose 54 may be transferred to the first refrigerant pipe 150 as much as possible without being wasted to the surroundings.

Since the fan 80 illustrated in FIGS. 9 and 10 causes forced convection heat transfer between the outer-side part 310 and the air in the machine room 2, the efficiency of cooling the refrigerant in the outer-side part 310 may be enhanced.

Heat exchange occurs between the outer-side part 310 and the inner-side part 320 by conduction, while heat exchange occurs between the outer-side part 310 and the air in the machine room by convection.

The flow direction of the refrigerant in the outer-side part 310 may be opposite to the flow direction of the water in the inner-side part 320. Since the refrigerant and the water in the outer-side part 310 and the inner-side part 320 flows in different directions, better heat exchange may occur between the outer-side part 310 and the inner-side part 320. Herein, flow of water in the inner-side part 320 occurs when the dispenser 40 or the ice maker 26 is used, and stops when neither of the dispenser 40 and the ice maker 26 is used.

When flow of water occurs in the inner-side part 320, the cooling efficiency of the refrigerant passing through the outer-side part 310 may be enhanced.

Particularly, the outer-side part 310 and the inner-side part 320 may be concentrically arranged. That is, the inner-side part 320 may be formed in the shape of a hollow cylinder, and the outer-side part 310 may be formed in the shape of a hollow cylinder having a larger diameter than the inner-side part 320 and having the inner-side part 320 positioned at the center thereof. Alternatively, the outer-side part 310 and the inner-side part 320 may have a different configuration such that the area of contact therebetween is increased with the area of cross section kept constant.

The first refrigerant pipe 150 may be perpendicularly connected to the outer-side part 310. That is, as shown in FIG. 11, the flow path of the refrigerant moving along the outer-side part 310 may be arranged perpendicular to the flow path of the refrigerant introduced into or discharged from the outer-side part 310 from/to the first refrigerant pipe 150. That is, since the flow path of the refrigerant introduced into the outer-side part 310 is perpendicular with respect to the outer-side part 310, sufficient heat exchange may occur between the refrigerant and the surface forming the external shape of the outer-side part 310 due to various types of flows.

In the heat exchange unit 300, the refrigerant moving along the outer-side part 310 and the water moving along the inner-side part 320 make contact or surface contact with each other at plural points. Accordingly, the efficiency of heat exchange may be enhanced.

In addition, since the heat exchange unit 300 is formed as a single component, separation of the first refrigerant pipe 150 from the first water hose 52 and the second water hose 54 due to vibration possibly caused by movement of the refrigerant or water may be prevented, compared to the case in which the first refrigerant pipe 150 is attached to the first water hose 52 and the second water hose 54 through welding.

Hereinafter, operation of the heat exchange unit 300 will be described based on the principle of movement of water according to one embodiment as broadly described herein.

First, the hot refrigerant compressed by the compression unit 110 is guided to the first refrigerant pipe 150. Then, the refrigerant flows along the first refrigerant pipe 150 and passes through the outer-side part 310 of the heat exchange unit 300. Accordingly, the temperature of the outer-side part 310 may be increased due to the temperature of the refrigerant, and may be partially lowered by heat exchange with the air in the machine room 2. At this time, the fan 80 is driven to cause forced convection between the inner space of the machine room 2 and the outer-side part 310. Thereby, the outer-side part 310 may be cooled by convection.

Compared to a case in which the above described heat exchange unit 300 is not provided, the area of the outer-side part 310 that contacts the air in the machine room 2 increases, and therefore the efficiency of cooling by convection may be improved. This is because the outer-side part 310 is arranged to surround the inner-side part 320, thereby having an increased area of contact with the air in the machine room 2.

After being discharged from the outer-side part 310, the refrigerant may be guided to the condensation unit 120 through the first refrigerant pipe 150 and condensed in the condensation unit 120. Then, the refrigerant may supply coldness thereof to the refrigeration compartment or the freezer compartment while passing through the capillary tube 130 and the evaporation unit 140. The refrigerant may supply coldness to the external area by being cooled to about −20 degrees Celsius in the evaporation unit 140. At this time, the compression unit 110 is driven, and thus the water contained in the inner-side part 320 may remain stationary or flow while the refrigerant circulates in the refrigeration cycle.

For example, in the case in which water is not dispensed using the dispenser 40, or the ice maker 26 does not need to produce ice, the flow path of the flow path control valve 33 is kept in a closed state, and the water supply valve 12 also closes the flow path. Accordingly, water remains stationary in the inner-side part 320.

However, as the inner-side part 320 is filled with water, heat exchange may occur between the inner-side part 320 and the outer-side part 310.

On the other hand, in the case in which water is dispensed using the dispenser 40, or the ice maker 26 needs to produce ice, the flow path of the flow path control valve 33 is opened, and the water supply valve 12 also opens the flow path. Accordingly, water flows from the external water source 50 into the inner-side part 320.

Thereby, flow of water occurs in the inner-side part 320, and the water and the refrigerant flow independently through the heat exchange unit 300, exchanging heat with each other. Thereby, the refrigerant is cooled while passing through the heat exchange unit 300.

The flow path control valve 33 may simultaneously supply water to both the dispenser 40 and the ice maker 26, or supply water to only one of the dispenser 40 or the ice maker 26. In either of these two cases, one flow path of the flow path control valve 33 is opened, and the flow path of the water supply valve 12 is also opened. Accordingly, flow of water may occur in the inner-side part 320.

Even when the compression unit 110 is not driven, water may be dispensed using the dispenser 40 or the ice maker 26 may need to produce ice. In this case, flow of water may occur in the inner-side part 320 and thus the refrigerant accommodated in the outer-side part 310 may be cooled. In addition, the water in the inner-side part 320 the temperature of which is substantially increased may be replaced by the water from the external water source 50 which is at a relatively low temperature. Accordingly, the operational efficiency of the refrigerator may be enhanced.

Since the inner-side part 320 and the outer-side part 310 contact each other at plural points through surface contact, the water passing through the inner-side part 320 may efficiently cool the refrigerant passing through the outer-side part 310.

In experimentation with the heat exchange unit 300, it has been found that the power consumption may be improved by about 3.9%. Specifically, in the case in which a heat exchange unit as embodied and broadly described herein was not adopted, 62.2 watts (W) was needed to operate the refrigeration cycle. In contrast, when the heat exchange unit 300 was adopted, 59.8 W was needed to operate the refrigeration cycle.

FIGS. 12 and 13 illustrate a machine room implemented in a different manner from that of FIG. 8. Hereinafter, a description will be given with reference to FIGS. 12 and 13. In FIGS. 12 and 13, pipes through which the refrigerant moves and other components unnecessary for the description are omitted for simple and clear illustration.

Unlike the previous embodiment, the heat exchange unit 300 according to this embodiment is installed in a space of the body 1 sealed by an insulation member, rather than in the machine room 2. Other elements may be substantially the same as those of the previous embodiment. Accordingly, the description given below is focused on the details different from the previous embodiment, and a description of the elements discussed above will be omitted.

A part of the first refrigerant pipe 150 to guide the refrigerant to the heat exchange unit 300, the first water hose 52 to supply water to the heat exchange unit 300, and a part of the second water hose 54 to discharge water from the heat exchange unit 300 are installed in a space sealed by an insulation member. In this embodiment, the outer-side part 310 is not exposed to the interior of the machine room 2, and therefore the outer-side part 310 is not cooled by the air in the machine room 2 through convection. However, since the inner-side part 320 through which water passes is installed in the sealed space, a larger portion of coldness may be used to cool the refrigerant passing through the outer-side part 310 without being used to cool the inner space of the machine room 2.

FIG. 14 illustrates a refrigeration cycle according to another embodiment.

In the embodiment illustrated in FIG. 14, the heat exchange unit 300 is installed at the third refrigerant pipe 170 extending from the condensation unit 120 and introduced into the capillary tube 130. The other elements and operation thereof may be substantially the same as those of the previous embodiment.

Since the refrigerant from the condensation unit 120 flows through the third refrigerant pipe 170, the temperature of the refrigerant flowing through the third refrigerant pipe 170 may be lower than the temperature of the refrigerant flowing into the condensation unit 120 through the first refrigerant pipe 150. In this case, the degree of decrease in temperature of the refrigerant by water may be lowered. On the other hand, since the increase in temperature of the water passing through the heat exchange unit 300 is small, the water may be less influenced.

The heat exchange unit 300 shown in FIG. 14 may be installed in the machine room 2. Alternatively, the heat exchange unit 300 may be installed in a space of the body 1 sealed by an insulation member instead of the machine room 2.

The heat exchange unit 300 is provided with the first water hose 52 and the second water hose 54 to allow water to flow into or out of the heat exchange unit 300. Accordingly, heat exchange occurs between the water and the refrigerant in the heat exchange unit 300, as described above in the previous embodiment. That is, heat exchange is performed in the same manner as in the previous embodiment, and thus some details as described above in the previous embodiment will be omitted for convenience of illustration.

FIG. 15 illustrates a refrigeration cycle according to another embodiment.

This embodiment employs two compression units 112 and 114, or two compressors 112 and 114. The other components are substantially the same as those of the previous embodiment illustrated in FIG. 7, and thus a description thereof will be omitted.

In this embodiment, a first compression unit 112 primarily compress the refrigerant guided thereinto from the evaporation unit 140, and a second compression unit 114 may secondarily compress the refrigerant compressed by the first compression unit 112 and guide the same to the condensation unit 120. After being compressed by the first compression unit 112, the refrigerant is additionally compressed while passing through the second compression unit 114. The compressed gaseous refrigerant may be supplied to the condensation unit 120. While the refrigerant passes through the second compression unit 114, the pressure thereof is increased. Accordingly, the temperature of the refrigerant guided from the second compression unit 114 to the condensation unit 120 may be higher than in any other components of the refrigeration cycle. Therefore, by installing the heat exchange unit 300 at the first refrigerant pipe 150 which remains at a relatively high temperature and lowering the temperature of the refrigerant through heat exchange between water and the refrigerant, the overall efficiency of the refrigeration cycle may be enhanced.

A description will now be provided of a refrigerator having a refrigeration cycle according to another embodiment, with reference to FIG. 16. In this embodiment, the refrigeration cycle includes the compression unit 110, the condensation unit 120, the capillary tube 130, and the evaporation unit 140, which are connected to each other by refrigerant pipes. A first refrigerant pipe 150 connects the compression unit 110 to the condensation unit 120, a second refrigerant pipe 160 connects the evaporation unit 140 to the compression unit 110, and a third refrigerant pipe 170 connects the condensation unit 120 to the capillary tube 130. The refrigerant is guided from the compression unit 110 to the condensation unit 120 through the first refrigerant pipe 150, guided from the evaporation unit 140 to the compression unit 110 through the second refrigerant pipe 160, and guided from the condensation unit 120 to the capillary tube 130 through the third refrigerant pipe 170.

The refrigerator may also include a first heat exchange unit 200, in which the first refrigerant pipe 150 and the second refrigerant pipe 160 contact each other to allow the refrigerants therein to exchange heat with each other, a second heat exchange unit 300, in which the first refrigerant pipe 150 or the third refrigerant pipe 170 contacts water to cool the refrigerant therein, and a water supply valve 12 (see FIG. 7) to supply water to the second heat exchange unit 300.

In the first heat exchange unit 200, the first refrigerant pipe 150 and the second refrigerant pipe 160 are arranged to contact each other such that the refrigerant passing through the first refrigerant pipe 150 exchanges heat with the refrigerant passing through the second refrigerant pipe 160.

In the second heat exchange unit 300, to allow heat exchange to occur between the refrigerant passing through the third refrigerant pipe 170 and water supplied through the water hoses 52 and 54, the third refrigerant pipe 170 is arranged to contact the water hoses.

Details of the first heat exchange unit 200 and the second heat exchange unit 300 have been described above, and thus a description thereof will be omitted.

While the second heat exchange unit 300 is illustrated in FIG. 16 as being disposed at the third refrigerant pipe 170, it may be disposed at the first refrigerant pipe 150.

In experimentation, a refrigerator in accordance with this embodiment including both the first heat exchange unit 200 and the second heat exchange unit 300, it was found that power consumption may be improved by about 8.5%. Specifically, in a case in which the heat exchange units 200 and 300 were not adopted, 62.2 watts (W) was needed to operate the refrigeration cycle. In contrast, when both the first heat exchange unit 200 and the second heat exchange unit 300 were adopted, 56.9 W was needed to operate the refrigeration cycle. This result may be due to a combination of the enhanced efficiency of the refrigeration cycle by the first heat exchange unit 200 and the enhanced efficiency of the refrigeration cycle by the second heat exchange unit 300.

According to one embodiment, operational efficiency of the refrigerator as broadly described herein may be enhanced, and accordingly energy may be saved.

According to one embodiment, using coldness of the refrigerant flowing into the compression unit after cooling the surroundings in the evaporation unit, the refrigerant guided from the compression unit to the condensation unit may be cooled. Accordingly, coldness of the refrigerant may be efficiently used without being wasted.

In addition, according to one embodiment, the refrigerant flowing into the compression unit may be cooled by the air in the machine room. Accordingly, overloading of the compression unit due to heat may be prevented.

According to one embodiment, the temperature of the refrigerant flowing into or out of the condensation unit may be lowered. Thereby, the efficiency of the refrigeration cycle may be enhanced.

According to one embodiment, a separate drive unit to operate to lower the temperature of the refrigerant is not needed. The interior of the refrigerator may be simplified.

A refrigerator is provided which has an improved operational efficiency.

A refrigerator is provided that allows heat exchange to occur between different portions of a refrigerant circulating in the refrigeration cycle, thereby increasing the temperature of the refrigerant entering a compression unit and decreasing the temperature of the refrigerant entering a condensation unit.

A refrigerator is provided that may enhance the refrigeration cycle by decreasing the temperature of the refrigerant entering or leaving a condensation unit.

A refrigerator, as embodied and broadly described herein, may include a compression unit to compress a refrigerant, a condensation unit to condense the refrigerant having passed through compression unit, a capillary tube unit to lower temperature and pressure of the refrigerant passing though the condensation unit, an evaporation unit to evaporate the refrigerant having passed through the capillary tube unit, and a heat exchange unit combined to a refrigerant pipe connected from the compression unit to cool the refrigerant in the refrigerant pipe.

The heat exchange unit may be configured to allow a first refrigerant pipe connecting the compression unit to the condensation unit and a second refrigerant pipe connecting the evaporation unit to the compression unit to contact each other to exchange heat with each other.

A refrigerant remaining at a relatively high temperature in a gaseous state may be present in the first refrigerant pipe, and a refrigerant remaining at a relatively low temperature in a gaseous state may be present in the second refrigerant pipe.

The heat exchange unit may be disposed in a machine room having the compression unit installed therein to contact air in the machine room.

The refrigerator according to claim 2, wherein the heat exchange unit may include an outer-side part connected to the first refrigerant pipe, and an inner-side part connected to the second refrigerant pipe, wherein the outer-side part may be arranged to surround the inner-side part.

A direction of flow of the refrigerant in the outer-side part may be opposite to a direction of flow of the refrigerant in the inner-side part.

The second refrigerant pipe may be perpendicularly connected to the outer-side part.

In the heat exchange unit, heat exchange occurs between the refrigerant guided from the compression unit to the condensation unit and the refrigerant guided from the evaporation unit to the compression unit.

The refrigerator may further include a water supply valve to supply water to the heat exchange unit, wherein the heat exchange unit may allow the refrigerant pipe entering or leaving the condensation unit to contact water to cool the refrigerant in the refrigerant pipe.

The water supply valve may be connected to an external water source to supply water from the external water source into the refrigerator or to interrupt supply of the water into the refrigerator.

The water having passed through the heat exchange unit may be supplied to a dispenser or an ice maker, wherein, when the water is supplied to the dispenser or the ice maker, a flow path of the water supply valve may be opened, and the water may flow through the heat exchange unit.

The refrigerator may further include a flow path control valve to guide the water having passed through the heat exchange unit such that the water may move to the dispenser or the ice maker.

The heat exchange unit may include an outer-side part allowing the refrigerant to pass therethrough, and an inner-side part allowing water to pass therethrough, wherein the outer-side part may be arranged to surround the inner-side part.

The refrigerant guided to the outer-side part may be introduced into and discharged from the outer-side part in a direction perpendicular to the outer-side part.

The refrigerator heat exchange unit may be installed to be exposed to the machine room having the compression unit installed therein to exchange heat with air in the machine room.

The heat exchange unit may be installed in a space sealed by an insulation member formed in a body of the refrigerator through foaming.

The refrigerator according to claim 1, wherein the compression unit may include a first compression unit to primarily compress the refrigerant guided from the evaporation unit, and a second compression unit to secondarily compress the refrigerant compressed by the first compression unit and guide the compressed refrigerant to the condensation unit.

In another embodiment as broadly described herein, a refrigerator may include a compression unit to compress a refrigerant, a condensation unit to condense the refrigerant having passed through compression unit, a capillary tube unit to lower temperature and pressure of the refrigerant passing though the condensation unit, an evaporation unit to evaporate the refrigerant having passed through the capillary tube unit, a first refrigerant pipe to connect the compression unit to the condensation unit, a second refrigerant pipe to connect the evaporation unit to the compression unit, a third refrigerant pipe to connect the condensation unit to the capillary tube unit, a first heat exchange unit allowing the first refrigerant pipe and the second refrigerant pipe to contact each other such that heat exchange occurs between the refrigerants in the first refrigerant pipe and the second refrigerant pipe, a second heat exchange unit allowing the first refrigerant pipe or the third refrigerant pipe to contact water to cool the refrigerant in the first refrigerant pipe or the third refrigerant pipe, and a water supply valve to supply water to the second heat exchange unit.

The first heat exchange unit may include an outer-side part connected to the first refrigerant pipe, and an inner-side part connected to the second refrigerant pipe and surrounded by the outer-side part.

The second heat exchange unit may include an outer-side part allowing the refrigerant to pass therethrough, and an inner-side part surrounded by the outer-side part and allowing water to pass therethrough.

Any reference in this specification to “one embodiment,” “an embodiment,” “example embodiment,” etc., means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the invention. The appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment. Further, when a particular feature, structure, or characteristic is described in connection with any embodiment, it is submitted that it is within the purview of one skilled in the art to effect such feature, structure, or characteristic in connection with other ones of the embodiments.

Although embodiments have been described with reference to a number of illustrative embodiments thereof, it should be understood that numerous other modifications and embodiments can be devised by those skilled in the art that will fall within the spirit and scope of the principles of this disclosure. More particularly, various variations and modifications are possible in the component parts and/or arrangements of the subject combination arrangement within the scope of the disclosure, the drawings and the appended claims. In addition to variations and modifications in the component parts and/or arrangements, alternative uses will also be apparent to those skilled in the art. 

What is claimed is:
 1. A refrigerator, comprising: a compressor configured to compress a refrigerant; a configured to receive refrigerant compressed by the compressor and to condense the received refrigerant; a capillary tube configured to receive refrigerant condensed by the condenser and to lower a temperature and a pressure of the received refrigerant; an evaporator configured to receive refrigerant from the capillary tube and to evaporate the received refrigerant; and a heat exchanger coupled to a refrigerant pipe connected to the compressor and configured to cool refrigerant in the refrigerant pipe.
 2. The refrigerator of claim 1, further comprising: a first refrigerant pipe connecting the compressor to the condenser; and a second refrigerant pipe connecting the evaporator to the compressor, wherein the first and second refrigerant pipes are each coupled to the heat exchanger such that refrigerant flowing through the first and second refrigerant pipes perform heat exchange with each other.
 3. The refrigerator of claim 2, wherein refrigerant at a relatively high temperature in a gaseous state flows in the first refrigerant pipe, and refrigerant at a relatively low temperature in a gaseous state flows in the second refrigerant pipe.
 4. The refrigerator of claim 2, wherein the heat exchanger is received in a machine room of the refrigerator having the compressor installed therein, so as to contact air in the machine room.
 5. The refrigerator of claim 2, wherein the heat exchanger comprises: an outer portion connected to the first refrigerant pipe; and an inner portion connected to the second refrigerant pipe, wherein the outer portion surrounds the inner portion.
 6. The refrigerator of claim 5, wherein the outer portion and the inner portion of the heat exchanger are concentrically arranged.
 7. The refrigerator of claim 5, wherein a refrigerant flow direction through the outer portion of the heat exchanger is opposite a refrigerant flow direction through the inner portion of the heat exchanger.
 8. The refrigerator of claim 7, wherein the second refrigerant pipe is oriented perpendicular to the outer portion.
 9. The refrigerator of claim 2, wherein, in the heat exchanger, heat exchange occurs between refrigerant flowing from the compressor to the condenser, and refrigerant flowing from the evaporator to the compressor.
 10. The refrigerator of claim 1, further comprising a water supply valve configured to supply water to the heat exchanger, wherein refrigerant received in the first refrigerant pipe coupled to the condenser to perform heat exchange with the water supplied by the water supply valve to cool the refrigerant in the second refrigerant pipe.
 11. The refrigerator of claim 10, wherein the water supply valve is connected to an external water source and is configured to supply water from the external water source to the refrigerator, or to interrupt the supply of water to the refrigerator.
 12. The refrigerator of claim 10, further comprising a dispenser and an ice maker each operably coupled in the refrigerator, wherein water that has passed through the heat exchanger is supplied to at least one of the dispenser or the ice maker, and wherein, when the water is supplied to the at least one of the dispenser or the ice maker, a flow path of the water supply valve is opened, and the water flows through the heat exchanger.
 13. The refrigerator of claim 12, further comprising a flow path control valve to guide the water that has passed through the heat exchanger to the dispenser or the ice maker.
 14. The refrigerator of claim 10, wherein the heat exchanger comprises: an outer portion forming a refrigerant flow path allowing refrigerant to flow therethrough; and an inner-portion forming a water flow path allowing water to flow therethrough, wherein the outer portion surrounds the inner portion.
 15. The refrigerator of claim 14, wherein the outer portion and the inner portion of the heat exchanger are concentrically arranged.
 16. The refrigerator of claim 14, wherein refrigerant guided to the outer portion of the heat exchanger is introduced into and discharged from the outer portion in a first direction, and water guided to the inner portion of the heat exchanger is introduced into and discharged from the inner portion in a second direction that is perpendicular to the first direction.
 17. The refrigerator of claim 14, wherein the heat exchanger is installed so as to be exposed in a machine room of the refrigerator having the compressor installed therein so as to exchange heat with air received in the machine room.
 18. The refrigerator of claim 14, wherein the heat exchanger is installed in a space formed in a body of the refrigerator that is sealed by a foamed insulation member.
 19. The refrigerator of claim 1, wherein the compressor comprises: a first compression device that performs primary compression of refrigerant received from the evaporator; and a second compression that performs secondary compression of refrigerant compressed by the first compression device and that guides the refrigerant having undergone primary and secondary compression to the condenser.
 20. A refrigerator comprising: a compressor configured to compress a refrigerant; a condenser configured to condense refrigerant received from the compressor; a capillary tube configured to lower a temperature and a pressure of refrigerant received from the condenser; an evaporator configured to evaporate refrigerant received from the capillary tube; a first refrigerant pipe that connects the compressor to the condenser; a second refrigerant pipe that connects the evaporator to the compressor; a third refrigerant pipe that connects the condenser to the capillary tube; a first heat exchanger that performs heat exchange between refrigerant flowing through the first refrigerant pipe and refrigerant flowing through the second refrigerant pipe; a second heat exchanger that performs heat exchange between refrigerant flowing through one of the first refrigerant pipe or the third refrigerant pipe and water to cool the refrigerant in the one of first refrigerant pipe or the third refrigerant pipe; and a water supply valve that supplies water to the second heat exchanger.
 21. The refrigerator of claim 20, wherein the first refrigerant pipe and the second refrigerant pipe contact each other in the first heat exchanger, and wherein the one of the first refrigerant pipe or the third refrigerant pipe contacts the water supplied by the water supply valve in the second heat exchanger.
 22. The refrigerator of claim 20, wherein the first heat exchanger comprises: an outer portion connected to the first refrigerant pipe; and an inner portion connected to the second refrigerant pipe and surrounded by the outer portion.
 23. The refrigerator of claim 20, wherein the second heat exchanger comprises: an outer portion allowing the refrigerant to pass therethrough; and an inner portion surrounded by the outer portion and allowing water to pass therethrough. 